US20080210895A1 - Pressure Relieved Thermal Regulator for Air Conditioning Application - Google Patents
Pressure Relieved Thermal Regulator for Air Conditioning Application Download PDFInfo
- Publication number
- US20080210895A1 US20080210895A1 US11/955,989 US95598907A US2008210895A1 US 20080210895 A1 US20080210895 A1 US 20080210895A1 US 95598907 A US95598907 A US 95598907A US 2008210895 A1 US2008210895 A1 US 2008210895A1
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- US
- United States
- Prior art keywords
- fluid
- opening
- chamber
- actuator
- control valve
- Prior art date
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Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D23/00—Control of temperature
- G05D23/01—Control of temperature without auxiliary power
- G05D23/02—Control of temperature without auxiliary power with sensing element expanding and contracting in response to changes of temperature
- G05D23/021—Control of temperature without auxiliary power with sensing element expanding and contracting in response to changes of temperature the sensing element being a non-metallic solid, e.g. elastomer, paste
- G05D23/023—Control of temperature without auxiliary power with sensing element expanding and contracting in response to changes of temperature the sensing element being a non-metallic solid, e.g. elastomer, paste the sensing element being placed outside a regulating fluid flow
Definitions
- This invention relates generally to the field of heat transfer and, more particularly, to a pressure relieved thermal regulator for air conditioning application.
- a variety of different heat transfer systems use water or other fluids to transfer heat or thermal energy between one or more production units and one or more loads. Such systems are often referred to as hydronic systems.
- a control valve for regulating temperature comprises a conduit, a fluid limiter, a restoring actuator, an opening actuator, and a restoring actuator chamber.
- the conduit has an inlet, an outlet, and an opening between the inlet and the outlet.
- the inlet is operable to receive fluid into the conduit and the outlet is operable to dispense of fluid out of the conduit.
- the fluid limiter is operable to at least partially cover the opening and thereby resist flow of fluid through the opening.
- the restoring actuator is operable to provide a force that moves the fluid limiter toward the opening to resist flow of fluid through the opening.
- the opening actuator is operable to provide a second force that moves the fluid limiter away from the opening to allow the flow of fluid through the opening.
- the opening actuator is activated based on a temperature of fluid in the conduit.
- the restoring actuator chamber is disposed around the restoring actuator and has a passage in communication with fluid upstream of the opening.
- a technical advantage of one embodiment may include the capability to choose the temperature of regulation so that a particular heat exchanger always receives the appropriate amount of coolant flow under variable loading conditions.
- Other technical advantages of other embodiments may include the capability to regulate the temperature of the fluid based on a setting despite pressure fluctuations.
- Still another technical advantage of other embodiments may include the capability for the thermal actuator to be changed without creating an opening from the water to the surrounding air, thereby allowing this operation to be done without shutting down the surrounding pipework.
- FIG. 1 is an example system in which embodiments of the invention may be utilized.
- FIG. 2 is a control valve, according to an embodiment of the invention.
- FIG. 1 is an example system in which embodiments of the invention may be utilized.
- Embodiments of the invention may apply to hydronic cooling systems, sometimes known as “chilled water” systems.
- a chiller provides cold fluid (e.g., including, but not limited to, water) to many different heat transfer terminals through a network of piping.
- the cold fluid rises in temperature as it passes through the various terminal units, as a result of heat or thermal energy being removed from various “loads.” That is, the thermal energy is transferred to the fluid.
- loads can include, but are not limited to, air in rooms of buildings or various industrial processes.
- fans associated with terminals may either change in speed or turn on and off in response, for example, to the temperature of a particular room in a building.
- a control valve may be used to maintain a constant temperature of fluid returning from the terminal.
- An example of such a valve is described below in the embodiment of FIG. 2 .
- the result in particular embodiments may be an extremely low flow of fluid when there is no load on the terminal (such as when the fan speed was slow or the fan was off) and an increased flow of fluid with an increased load.
- the control valve 100 in this embodiment includes a valve housing 200 and an actuator housing 300 .
- the valve housing 200 contains components, which facilitate the closing of an opening 250 in the valve housing and the actuator housing 300 include components which facilitate the opening of the opening 250 .
- the valve housing 200 include a conduit body 205 , obstructions 210 , 220 , and 230 ; a plunger 240 ; an opening 250 ; a restoring spring 260 ; and a communication rod 270 .
- the obstructions 210 , 220 , and 230 work against a flow of fluid (indicated by arrows 280 ) through the valve housing 200 while the opening 250 allows the flow of fluid (indicated by arrows 280 ) through the valve housing 200 .
- the plunger 240 selectively covers the opening 250 upon receiving force from one or both of the force of the restoring spring 260 and an external force communicated through the communication rod 270 .
- the communication rod 270 is in communication with the actuator housing 300 .
- the communication rod 270 communicates the temperature of the fluid to the actuator housing 300 .
- the communication rod 270 may be brass or other type of metal operable to conduct thermal energy.
- a seal 207 between a wall 203 of the conduit body 205 and the communication rod 270 .
- the seal 207 allows axial movement of the communication rod 270 while preventing entry of fluid into the actuator housing 300 This creates the possibility of replacing the actuator housing 300 , along with the associated components 305 , 310 . 320 , 330 , 340 , and 350 , without having to isolate the valve housing 200 from the surrounding pipework.
- the actuator housing 300 includes a housing body 305 , a chamber 310 , a piston rod 320 , limiters 330 , a limiter stop 340 , and an overtravel spring 350 .
- the housing body 305 is threadingly engaged with the conduit body 205 .
- this threading engagement allows an initial setting of the position of the communication rod 270 .
- the chamber 310 includes a heat sensitive substance operable change volume when subjected to a change in temperature.
- the heat sensitive substance may comprise water, oil, wax, or other suitable substances, including combinations thereof.
- heat sensitive substance may comprise an alkane hydrocarbon.
- heat sensitive substance comprises a mixture of different types of paraffin having different melting points.
- the piston rod 320 extends into and out of the chamber as the mixture of paraffin melts or solidifies.
- the overtravel spring 350 resists the piston rod 320 , causing the chamber 310 and communication rod 270 to be pushed down when the piston rod 320 exits the chamber 310 .
- the overtravel spring 350 is coupled to a limiter stop 340 , which are resisted by limiters 330 .
- the overtravel spring 350 compensates for such “overtravel” by compressing and allowing the combination of the piston rod 320 to move up when chamber 310 and communication rod 270 can no longer move down. This action prevents excessive pressure from building up inside chamber 310 .
- the initial set point of the communication rod 270 is set by the amount of threading between the housing body 305 and the conduit body 205 .
- the increase in the thermal energy is communicated through the communication rod 270 up to the chamber 310 in the actuator housing 300 .
- the volume inside the chamber 310 increases, thereby forcing the piston rod 320 out of the chamber 310 .
- the resistance to the piston rod 320 by the overtravel spring 350 forces the chamber 310 and communication rod 270 downward to push the plunger 240 out of the way of the opening 250 .
- the downward movement of the plunger 240 compresses the restoring spring 260 .
- This operation in particular embodiments can allow a fixed, desired return water temperature on the downstream side of the opening 250 . That is, until the desired temperature of the fluid is reached, the mixture of paraffin in the chamber 310 won't melt (from thermal energy communicated from the communication rode 270 ) and the plunger 240 will not be moved out the way of the opening 250 .
- the result as in particular embodiments as indicated above may be an extremely low flow of fluid when there is no load on the terminal (such as when the fan speed was slow or the fan was off) and an increased flow of fluid with an increased load.
- the mixture of paraffins may be designed so that melting takes place over a range of temperatures, with the total travel of the actuator being greater than the travel required to open or close the valve.
- the temperature of regulation may be set by adjusting the threading engagement between actuator housing 305 and conduit housing 205 .
- This pressure acting on the opposite face of plunger 240 counteracts the pressure from opening 250 , thereby allowing the valve to function at differential pressures much higher than otherwise would be possible.
- control valve 100 Modifications, additions, or omissions may be made to the control valve 100 .
- the components of the control valve 100 may be integrated or separated according to particular needs.
- the operations of the control valve 100 may be performed by more, fewer, or other components.
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Temperature-Responsive Valves (AREA)
Abstract
Description
- Pursuant to 35 U.S.C. § 119 (e), this application claims priority to U.S. Provisional Patent Application Ser. No. 60/870,016, entitled PRESSURE RELIEVED THERMAL REGULATOR FOR AIR CONDITIONING APPLICATION filed Dec. 14, 2006. U.S. Provisional Patent Application Ser. No. 60/870,016, is hereby incorporated by reference.
- This invention relates generally to the field of heat transfer and, more particularly, to a pressure relieved thermal regulator for air conditioning application.
- A variety of different heat transfer systems use water or other fluids to transfer heat or thermal energy between one or more production units and one or more loads. Such systems are often referred to as hydronic systems.
- According to one embodiment of the invention, a control valve for regulating temperature comprises a conduit, a fluid limiter, a restoring actuator, an opening actuator, and a restoring actuator chamber. The conduit has an inlet, an outlet, and an opening between the inlet and the outlet. The inlet is operable to receive fluid into the conduit and the outlet is operable to dispense of fluid out of the conduit. The fluid limiter is operable to at least partially cover the opening and thereby resist flow of fluid through the opening. The restoring actuator is operable to provide a force that moves the fluid limiter toward the opening to resist flow of fluid through the opening. The opening actuator is operable to provide a second force that moves the fluid limiter away from the opening to allow the flow of fluid through the opening. The opening actuator is activated based on a temperature of fluid in the conduit. The restoring actuator chamber is disposed around the restoring actuator and has a passage in communication with fluid upstream of the opening.
- Certain embodiments of the invention may provide numerous technical advantages. For example, a technical advantage of one embodiment may include the capability to choose the temperature of regulation so that a particular heat exchanger always receives the appropriate amount of coolant flow under variable loading conditions. Other technical advantages of other embodiments may include the capability to regulate the temperature of the fluid based on a setting despite pressure fluctuations. Still another technical advantage of other embodiments may include the capability for the thermal actuator to be changed without creating an opening from the water to the surrounding air, thereby allowing this operation to be done without shutting down the surrounding pipework.
- Although specific advantages have been enumerated above, various embodiments may include all, some, or none of the enumerated advantages. Additionally, other technical advantages may become readily apparent to one of ordinary skill in the art after review of the following figures and description.
- For a more complete understanding of example embodiments of the present invention and its advantages, reference is now made to the following description, taken in conjunction with the accompanying drawings, in which:
-
FIG. 1 is an example system in which embodiments of the invention may be utilized; and -
FIG. 2 is a control valve, according to an embodiment of the invention. - It should be understood at the outset that although example embodiments of the present invention are illustrated below, the present invention may be implemented using any number of techniques, whether currently known or in existence. The present invention should in no way be limited to the example embodiments, drawings, and techniques illustrated below, including the embodiments and implementation illustrated and described herein. Additionally, the drawings are not necessarily drawn to scale.
-
FIG. 1 is an example system in which embodiments of the invention may be utilized. Embodiments of the invention may apply to hydronic cooling systems, sometimes known as “chilled water” systems. In such systems a chiller provides cold fluid (e.g., including, but not limited to, water) to many different heat transfer terminals through a network of piping. The cold fluid rises in temperature as it passes through the various terminal units, as a result of heat or thermal energy being removed from various “loads.” That is, the thermal energy is transferred to the fluid. These loads can include, but are not limited to, air in rooms of buildings or various industrial processes. In particular embodiments, fans associated with terminals may either change in speed or turn on and off in response, for example, to the temperature of a particular room in a building. In particular embodiments, a control valve may be used to maintain a constant temperature of fluid returning from the terminal. An example of such a valve is described below in the embodiment ofFIG. 2 . The result in particular embodiments may be an extremely low flow of fluid when there is no load on the terminal (such as when the fan speed was slow or the fan was off) and an increased flow of fluid with an increased load. -
FIG. 2 is acontrol valve 100, according to an embodiment of the invention. Thecontrol valve 100 ofFIG. 2 may be placed in a variety of locations including, but not limited to, between the terminal and the return header line shown inFIG. 1 . In particular embodiments, thecontrol valve 100 can be used to control the amount of return fluid flow provided to the return header line shown inFIG. 1 as a function of the temperature of the fluid provided to thecontrol valve 100. - The
control valve 100 in this embodiment includes avalve housing 200 and anactuator housing 300. Thevalve housing 200 contains components, which facilitate the closing of anopening 250 in the valve housing and theactuator housing 300 include components which facilitate the opening of theopening 250. - In the embodiment of
FIG. 2 , thevalve housing 200 include aconduit body 205,obstructions plunger 240; anopening 250; a restoringspring 260; and acommunication rod 270. In operation, theobstructions valve housing 200 while theopening 250 allows the flow of fluid (indicated by arrows 280) through thevalve housing 200. Theplunger 240 selectively covers the opening 250 upon receiving force from one or both of the force of the restoringspring 260 and an external force communicated through thecommunication rod 270. - The
communication rod 270 is in communication with theactuator housing 300. In the embodiment ofFIG. 2 , thecommunication rod 270 communicates the temperature of the fluid to theactuator housing 300. In particular embodiments thecommunication rod 270 may be brass or other type of metal operable to conduct thermal energy. - In this particular embodiments, there is a
seal 207 between awall 203 of theconduit body 205 and thecommunication rod 270. Theseal 207 allows axial movement of thecommunication rod 270 while preventing entry of fluid into theactuator housing 300 This creates the possibility of replacing theactuator housing 300, along with theassociated components valve housing 200 from the surrounding pipework. In other embodiments, there may not be a seal, thereby allowing fluid into theactuator housing 300. - In the embodiment of
FIG. 2 , theactuator housing 300 includes ahousing body 305, achamber 310, apiston rod 320,limiters 330, alimiter stop 340, and anovertravel spring 350. - The
housing body 305 is threadingly engaged with theconduit body 205. In particular embodiments, this threading engagement allows an initial setting of the position of thecommunication rod 270. - The
chamber 310 includes a heat sensitive substance operable change volume when subjected to a change in temperature. In particular embodiments, the heat sensitive substance may comprise water, oil, wax, or other suitable substances, including combinations thereof. In one embodiment, heat sensitive substance may comprise an alkane hydrocarbon. In the illustrated embodiment, heat sensitive substance comprises a mixture of different types of paraffin having different melting points. - The
piston rod 320 extends into and out of the chamber as the mixture of paraffin melts or solidifies. In this particular embodiment, when the mixture of paraffin melts, the volume—a characteristic of the heat sensitive substance—increases, causing thepiston rod 320 to move out of thechamber 310. - The
overtravel spring 350 resists thepiston rod 320, causing thechamber 310 andcommunication rod 270 to be pushed down when thepiston rod 320 exits thechamber 310. To avoidovertravel spring 350 from going too far downward, theovertravel spring 350 is coupled to alimiter stop 340, which are resisted bylimiters 330. In operation, when thechamber 310 andcommunication rod 270 can no longer move downward (for example, they have reached their maximum level), theovertravel spring 350 compensates for such “overtravel” by compressing and allowing the combination of thepiston rod 320 to move up whenchamber 310 andcommunication rod 270 can no longer move down. This action prevents excessive pressure from building up insidechamber 310. - In operation, the initial set point of the
communication rod 270 is set by the amount of threading between thehousing body 305 and theconduit body 205. As thermal energy received in the flow of fluid (indicated by arrows 280) increases, the increase in the thermal energy is communicated through thecommunication rod 270 up to thechamber 310 in theactuator housing 300. As the mixture of paraffin wax in thechamber 310 melts, the volume inside thechamber 310 increases, thereby forcing thepiston rod 320 out of thechamber 310. The resistance to thepiston rod 320 by theovertravel spring 350 forces thechamber 310 andcommunication rod 270 downward to push theplunger 240 out of the way of theopening 250. The downward movement of theplunger 240 compresses the restoringspring 260. - As temperature of the fluid decreases, the opposite occurs with the
piston rod 320 retracting into the chamber 310 (due to decreased volume in the now-solidifying mixture of paraffin) and the restoringspring 260 forcing movement of theplunger 240 back over theopening 250. - This operation in particular embodiments can allow a fixed, desired return water temperature on the downstream side of the
opening 250. That is, until the desired temperature of the fluid is reached, the mixture of paraffin in thechamber 310 won't melt (from thermal energy communicated from the communication rode 270) and theplunger 240 will not be moved out the way of theopening 250. The result as in particular embodiments as indicated above may be an extremely low flow of fluid when there is no load on the terminal (such as when the fan speed was slow or the fan was off) and an increased flow of fluid with an increased load. - In particular embodiments the mixture of paraffins may be designed so that melting takes place over a range of temperatures, with the total travel of the actuator being greater than the travel required to open or close the valve. In such embodiments, the temperature of regulation may be set by adjusting the threading engagement between
actuator housing 305 andconduit housing 205. - In particular embodiments there may be a
passage 255 which allows the pressure from the area of the valve upstream ofopening 250 to be transmitted into chamber 265 (around spring 260). This pressure acting on the opposite face ofplunger 240 counteracts the pressure from opening 250, thereby allowing the valve to function at differential pressures much higher than otherwise would be possible. - Modifications, additions, or omissions may be made to the
control valve 100. For example, the components of thecontrol valve 100 may be integrated or separated according to particular needs. Moreover, the operations of thecontrol valve 100 may be performed by more, fewer, or other components. - While this disclosure has been described in terms of certain embodiments and generally associated methods, alterations and permutations of the embodiments and methods will be apparent to those skilled in the art. Accordingly, the above description of example embodiments does not constrain this disclosure. Other changes, substitutions, and alterations are also possible without departing from the spirit and scope of this disclosure, as defined by the following claims.
Claims (31)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/955,989 US7909262B2 (en) | 2006-12-14 | 2007-12-13 | Pressure relieved thermal regulator for air conditioning application |
PCT/US2007/087533 WO2008076864A2 (en) | 2006-12-14 | 2007-12-14 | Pressure relieved thermal regulator air conditioning application |
EP07865674A EP2095200A2 (en) | 2006-12-14 | 2007-12-14 | Pressure relieved thermal regulator air conditioning application |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US87001606P | 2006-12-14 | 2006-12-14 | |
US11/955,989 US7909262B2 (en) | 2006-12-14 | 2007-12-13 | Pressure relieved thermal regulator for air conditioning application |
Publications (2)
Publication Number | Publication Date |
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US20080210895A1 true US20080210895A1 (en) | 2008-09-04 |
US7909262B2 US7909262B2 (en) | 2011-03-22 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/955,989 Expired - Fee Related US7909262B2 (en) | 2006-12-14 | 2007-12-13 | Pressure relieved thermal regulator for air conditioning application |
Country Status (3)
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US (1) | US7909262B2 (en) |
EP (1) | EP2095200A2 (en) |
WO (1) | WO2008076864A2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7909262B2 (en) * | 2006-12-14 | 2011-03-22 | Flow Design, Inc. | Pressure relieved thermal regulator for air conditioning application |
WO2016104948A1 (en) * | 2014-12-24 | 2016-06-30 | 인지컨트롤스주식회사 | Thermostat |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009055936A1 (en) | 2009-11-26 | 2011-06-09 | Theodor Heimeier Metallwerk Gmbh | Return temperature control valve for cooling systems |
US9933167B2 (en) | 2014-03-18 | 2018-04-03 | Imi Hydronic Engineering, Inc. | Retrofit smart components for use in a fluid transfer system |
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US1999732A (en) * | 1932-08-03 | 1935-04-30 | Milwaukee Gas Specialty Co | Thermostat control device |
US2308861A (en) * | 1940-02-06 | 1943-01-19 | Clifford Mfg Co | Temperature controlled valve |
US2495272A (en) * | 1947-07-17 | 1950-01-24 | Gen Electric | Inverse automatic flow regulating valve system |
US2547882A (en) * | 1945-04-30 | 1951-04-03 | Norton Orlo Clair | Means for regulating temperature and pressure operated valves |
US2577903A (en) * | 1947-08-20 | 1951-12-11 | Carrier Corp | Control bulb for thermal expansion valves |
US2579034A (en) * | 1945-06-08 | 1951-12-18 | Alco Valve Co | Multiple response override for thermal valves |
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US3838812A (en) * | 1971-06-04 | 1974-10-01 | C Johnson | Temperature responsive valve assembly |
US4158437A (en) * | 1974-12-16 | 1979-06-19 | Danfoss A/S | Thermostatic expansion valve for refrigeration plants |
US4214698A (en) * | 1977-11-21 | 1980-07-29 | Tour & Andersson Aktiebolag | Arrangement for control of the temperature of heat radiators in a co-tube system |
US4236669A (en) * | 1978-12-18 | 1980-12-02 | Borg-Warner Corporation | Thermostatic expansion valve with lead-lag compensation |
US4288033A (en) * | 1978-07-17 | 1981-09-08 | Century Brass Products, Inc. | Control valve assembly |
US4453668A (en) * | 1982-11-10 | 1984-06-12 | Caltherm Corporation | Fail-safe thermostatic valve |
US4557252A (en) * | 1983-04-15 | 1985-12-10 | Pulstar Corporation | Freeze protection valve and system |
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US20080041971A1 (en) * | 2006-08-18 | 2008-02-21 | Flow Design, Inc. | System and Method for Regulating Heat Transfer on a Fluid by Regulating the Flow of the Fluid |
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-
2007
- 2007-12-13 US US11/955,989 patent/US7909262B2/en not_active Expired - Fee Related
- 2007-12-14 WO PCT/US2007/087533 patent/WO2008076864A2/en active Application Filing
- 2007-12-14 EP EP07865674A patent/EP2095200A2/en not_active Withdrawn
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US1999732A (en) * | 1932-08-03 | 1935-04-30 | Milwaukee Gas Specialty Co | Thermostat control device |
US2308861A (en) * | 1940-02-06 | 1943-01-19 | Clifford Mfg Co | Temperature controlled valve |
US2547882A (en) * | 1945-04-30 | 1951-04-03 | Norton Orlo Clair | Means for regulating temperature and pressure operated valves |
US2579034A (en) * | 1945-06-08 | 1951-12-18 | Alco Valve Co | Multiple response override for thermal valves |
US2495272A (en) * | 1947-07-17 | 1950-01-24 | Gen Electric | Inverse automatic flow regulating valve system |
US2577903A (en) * | 1947-08-20 | 1951-12-11 | Carrier Corp | Control bulb for thermal expansion valves |
US2938384A (en) * | 1954-11-16 | 1960-05-31 | Controls Co Of America | Temperature-actuated power device |
US3111816A (en) * | 1958-11-07 | 1963-11-26 | Alco Valve Co | Thermostatic expansion valve with compound pressure regulating override |
US3838812A (en) * | 1971-06-04 | 1974-10-01 | C Johnson | Temperature responsive valve assembly |
US4158437A (en) * | 1974-12-16 | 1979-06-19 | Danfoss A/S | Thermostatic expansion valve for refrigeration plants |
US4214698A (en) * | 1977-11-21 | 1980-07-29 | Tour & Andersson Aktiebolag | Arrangement for control of the temperature of heat radiators in a co-tube system |
US4288033A (en) * | 1978-07-17 | 1981-09-08 | Century Brass Products, Inc. | Control valve assembly |
US4236669A (en) * | 1978-12-18 | 1980-12-02 | Borg-Warner Corporation | Thermostatic expansion valve with lead-lag compensation |
US4453668A (en) * | 1982-11-10 | 1984-06-12 | Caltherm Corporation | Fail-safe thermostatic valve |
US4557252A (en) * | 1983-04-15 | 1985-12-10 | Pulstar Corporation | Freeze protection valve and system |
US4883225A (en) * | 1988-03-18 | 1989-11-28 | S.T.C., Inc. | Fail-safe thermostat for vehicular cooling systems |
US4959973A (en) * | 1988-05-23 | 1990-10-02 | Fuji Koki Manufacturing Co., Ltd. | Thermostatic expansion valve |
US5018665A (en) * | 1990-02-13 | 1991-05-28 | Hale Fire Pump Company | Thermal relief valve |
US5257737A (en) * | 1990-12-28 | 1993-11-02 | Danfoss A/S | Thermostatic expansion valve for refrigerating plants |
US5984197A (en) * | 1998-02-12 | 1999-11-16 | C. Alan Sugarek | Thermostat |
US6299071B1 (en) * | 1999-06-19 | 2001-10-09 | Stadler Viega, Llc | Hydronic heating with continuous circulation |
US6565009B2 (en) * | 1999-07-19 | 2003-05-20 | Fujikoki Corporation | System for preventing hunting of expansion valve within refrigeration cycle |
US6360956B1 (en) * | 2000-03-01 | 2002-03-26 | Conbraco Industries, Inc. | Temperature-responsive mixing valve |
US7255286B2 (en) * | 2004-03-19 | 2007-08-14 | Carleton Technologies, Inc. | Temperature compensation valve |
US20060113399A1 (en) * | 2004-10-18 | 2006-06-01 | Thierry Maraux | Thermostatic valve for a fluid circuit, heat engine associated with a cooling circuit including such a valve, and method for manufacturing such a valve |
US20080041971A1 (en) * | 2006-08-18 | 2008-02-21 | Flow Design, Inc. | System and Method for Regulating Heat Transfer on a Fluid by Regulating the Flow of the Fluid |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7909262B2 (en) * | 2006-12-14 | 2011-03-22 | Flow Design, Inc. | Pressure relieved thermal regulator for air conditioning application |
WO2016104948A1 (en) * | 2014-12-24 | 2016-06-30 | 인지컨트롤스주식회사 | Thermostat |
Also Published As
Publication number | Publication date |
---|---|
EP2095200A2 (en) | 2009-09-02 |
WO2008076864A3 (en) | 2009-10-01 |
US7909262B2 (en) | 2011-03-22 |
WO2008076864A2 (en) | 2008-06-26 |
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